heat exchanger

Abstract

This heat exchanger provides high heat exchange efficiency while also offering good drainage. [Solution] The heat exchanger (1) comprises a plurality of plate-shaped fins (11) arranged at intervals from each other in the thickness direction, and a plurality of heat transfer tubes (12) that extend through each of the plurality of plate-shaped fins (11) in the thickness direction and are arranged at intervals from each other in a direction perpendicular to the thickness direction. The heat exchanger is installed with the parallel direction (Y) of the heat transfer tubes (12) being the vertical direction. Each of the plurality of fins has a heat transfer tube insertion portion that is open at one end edge in the direction of outside air flow (Z) perpendicular to both the extension direction (X) and the parallel direction (Y) of the heat transfer tubes and closed at the other end edge, and a stepped portion (S) that extends in the parallel direction of the heat transfer tubes and forms a step in the thickness direction between the other end edge of the plate-shaped fin (11) and the heat transfer tube insertion portion, and the distance between the heat transfer tube insertion portion and the stepped portion determined for each of the plurality of heat transfer tubes (12) is 3 mm or less.

Description

Technical Field

[0001] The present invention relates to a heat exchanger including plate fins and heat transfer tubes.

Background Art

[0002] There is a fin-tube type heat exchanger including a plurality of plate fins arranged at intervals from each other, and a plurality of heat transfer tubes extending in the direction in which these plurality of plate fins are arranged, penetrating each of the plurality of plate fins in its thickness direction, and arranged at intervals from each other in a direction perpendicular to the direction in which the plate fins are arranged.

[0003] [[ID=1's]] In Patent Document 1, with the direction in which outside air flows between heat transfer tubes as the outside air flow direction, in each of the plurality of plate fins, a notch that is long in the outside air flow direction and has an opening at one edge portion in the outside air flow direction is provided, and a heat exchanger in which each of the plurality of heat transfer tubes is inserted and arranged in these notches is disclosed.

Prior Art Documents

Patent Documents

[0004]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0005] When a heat transfer tube having a flat cross-sectional shape is adopted, an improvement in heat exchange efficiency can be expected as compared with the case where a heat transfer tube having another cross-sectional shape such as a circular cross-section is adopted. However, on the other hand, [[ID=4's]] During operation of the heat exchanger, water droplets formed by condensation tend to accumulate on the upper surface of the heat transfer tubes and are difficult to discharge from the heat exchanger. there were concerns. Furthermore, while it is expected that the heat exchange efficiency can be improved by forming slits in the plate-shaped fins where they are sandwiched between heat transfer tubes, it is necessary to ensure that the smooth flow of outside air between the heat transfer tubes is not impaired.

[0006] Therefore, the present invention In fin-tube type heat exchangers, aims to achieve Contributing to the realization of high heat exchange efficiency.

Means for Solving the Problems

[0007] To solve the aforementioned problems, a heat exchanger according to one embodiment of the present invention comprises a plurality of plate-shaped fins arranged at intervals from each other in the thickness direction, and a plurality of heat transfer tubes extending through each of the plurality of plate-shaped fins in the thickness direction and arranged at intervals from each other in a direction perpendicular to the thickness direction, wherein the plurality of heat transfer tubes are arranged in a parallel direction with the direction of parallelism of the heat transfer tubes being vertical. , a heat exchanger in which outside air flows between the heat transfer tubes arranged in the parallel direction. The plate-shaped fin is The aforementioned The plate-shaped fin has a heat transfer tube insertion portion that is open at one end edge in the direction of outside airflow and closed at the other end edge, and a stepped portion that extends in the parallel direction of the heat transfer tubes and forms a step in the thickness direction between the other end edge of the plate-shaped fin and the heat transfer tube insertion portion, The heat exchanger has a slit in the water storage region sandwiched between the heat exchanger tubes that are adjacent to each other in the parallel direction. The heat exchanger is provided as a fin tube assembly in which the plurality of heat exchanger tubes are assembled to penetrate each of the plurality of plate-shaped fins in the thickness direction, and a second fin tube assembly is provided in which the plurality of heat exchanger tubes different from those of the first fin tube assembly are assembled to each of the plurality of plate-shaped fins different from those of the first fin tube assembly, and the second fin tube assembly is positioned on one side of the first fin tube assembly in the direction of outside air flow, and the first water storage region, which is the water storage region having the slit, and the second water storage region, which is the water storage region without the slit, are arranged in a staggered pattern between the first fin tube assembly and the second fin tube assembly so as to be adjacent to each other in the direction of outside air flow when viewing the heat exchanger in a plan view in the parallel direction of the heat exchanger tubes. . Another embodiment of the present invention provides a heat exchanger comprising: a plurality of plate-shaped fins arranged at intervals from each other in the thickness direction; and a plurality of heat transfer tubes extending through each of the plurality of plate-shaped fins in the thickness direction and arranged at intervals from each other in a direction perpendicular to the thickness direction, wherein the plurality of heat transfer tubes are arranged in a parallel direction with the parallel direction of the heat transfer tubes being vertical, and outside air flows between the heat transfer tubes arranged in the parallel direction. The plate-shaped fins have a heat transfer tube insertion portion that is open at one end edge in the direction of outside air flow and closed at the other end edge, and a stepped portion that extends in the parallel direction of the heat transfer tubes and forms a step in the thickness direction between the other end edge of the plate-shaped fin and the heat transfer tube insertion portion, and have a slit in the water storage region sandwiched between the heat transfer tubes that are adjacent to each other in the parallel direction. The heat exchanger is provided with a first fin tube assembly, in which the plurality of heat transfer tubes are assembled to penetrate each of the plurality of plate-shaped fins in the thickness direction, and a second fin tube assembly, in which a plurality of heat transfer tubes different from those of the first fin tube assembly are assembled to each of the plurality of plate-shaped fins different from those of the first fin tube assembly. The second fin tube assembly is positioned on one side of the first fin tube assembly in the direction of the outside air flow, and a first water storage region having the slits and a second water storage region not having the slits are arranged in a staggered pattern between the first fin tube assembly and the second fin tube assembly so as to be adjacent to each other in the direction of the outside air flow when the heat exchanger is viewed from the side in the direction of the extension of the heat transfer tubes. [Effects of the Invention]

[0008] Thus, by employing a so-called fin-tube type heat exchanger, high heat exchange efficiency is achieved, In the plate-shaped fins, slits are formed in the water storage area sandwiched between heat transfer tubes arranged adjacently in a parallel direction, thereby improving heat exchange efficiency. This becomes possible. Here, a fin tube assembly is constructed by assembling multiple heat transfer tubes so that they penetrate each of the multiple plate-shaped fins in the thickness direction, and the first fin tube assembly and the second fin tube assembly are arranged in a staggered pattern such that the first water storage region and the second water storage region are adjacent to each other in the direction of outside air flow when viewed from the side or in a plan view of the heat exchanger. This makes it possible to maintain as much as possible the effect of improving heat exchange efficiency by providing slits, while suppressing the situation in which excessively large air resistance is generated by the slits, causing stagnation of airflow inside the heat exchanger. Furthermore, it is possible to equalize the air resistance exerted by the slits and suppress the situation in which unevenness occurs in the flow of outside air through the heat exchanger. [Brief explanation of the drawing]

[0009] [Figure 1] This is a schematic diagram showing the configuration of a refrigeration cycle system equipped with a heat exchanger according to one embodiment of the present invention (first embodiment). [Figure 2] This is a front view showing the configuration of the heat exchanger described above. [Figure 3] This is a schematic diagram showing the configuration of the fin tube assembly provided in the heat exchanger. [Figure 4] This is an explanatory diagram illustrating the effect of forming a stepped portion on a plate-shaped fin. [Figure 5] This is a schematic diagram showing the configuration of a fin tube assembly provided in a heat exchanger according to another embodiment (second embodiment) of the present invention. [Figure 6]It is a schematic diagram showing the configuration of a fin-tube assembly provided in a heat exchanger according to another embodiment (third embodiment) of the present invention. [Figure 7] It is a schematic diagram showing the configuration of a fin-tube assembly provided in a heat exchanger according to another embodiment (fourth embodiment) of the present invention. [Figure 8] It is a schematic diagram showing the configuration of a fin-tube assembly provided in a heat exchanger according to another embodiment (fifth embodiment) of the present invention. [Figure 9] It is a schematic diagram showing the configuration of a fin-tube assembly provided in a heat exchanger according to another embodiment (sixth embodiment) of the present invention.

Embodiments for Carrying Out the Invention

[0010] Hereinafter, embodiments of the present invention will be described with reference to the drawings.

[0011] (First Embodiment) FIG. 1 is a schematic diagram showing the configuration of a refrigeration cycle device C including a heat exchanger 1 according to the first embodiment of the present invention.

[0012] In the present embodiment, the heat exchanger 1 is configured as an outdoor heat exchanger and is disposed outdoors.

[0013] (Configuration of Refrigeration Cycle Device) The refrigeration cycle device C is configured as an air conditioner, and in addition to the heat exchanger 1, includes a compressor 2, a four-way valve 3, an expansion valve 4, and an indoor heat exchanger 5, and also includes a refrigerant pipe 6 (6a to 6f) for connecting these refrigeration cycle elements. The heat exchanger 1 is provided with an outdoor fan 1', and outdoor air (that is, outside air) is sent into the interior by the outdoor fan 1'. The indoor heat exchanger 5 is provided with an indoor fan 5', and indoor air is sent into the interior by the indoor fan 5'.

[0014] The compressor 2 comprises a compressor body 2a and an accumulator 2b. The accumulator 2b separates the gaseous and liquid refrigerants and supplies the separated gaseous refrigerant to the compressor body 2a. The compressor body 2a compresses the supplied gaseous refrigerant to produce high-temperature, high-pressure gaseous refrigerant.

[0015] The operation of the refrigeration cycle device C can be switched between cooling and heating operation by switching the flow path of the four-way valve 3.

[0016] (Air conditioning operation) Figure 1 shows the flow of refrigerant during cooling operation, indicated by the solid arrow A1.

[0017] During cooling operation, the refrigerant flows through the refrigerant piping 6 in the following order after exiting the compressor 2: four-way valve 3, heat exchanger 1, expansion valve 4, and indoor heat exchanger 5. The high-pressure gaseous refrigerant compressed by the compressor 2 is cooled and condensed by heat exchange with the outside air as it flows into the heat exchanger 1. The condensed gas-liquid mixed refrigerant has its pressure reduced as it passes through the expansion valve 4, becoming a low-pressure liquid refrigerant that is supplied to the indoor heat exchanger 5. The liquid refrigerant that flows into the indoor heat exchanger 5 is heated and evaporated by heat exchange with the indoor air, and the evaporated gas-liquid mixed refrigerant returns to the compressor 2 via the four-way valve 3.

[0018] (Heating operation) Figure 1 shows the flow of refrigerant during heating operation, indicated by the dotted arrow A2.

[0019] During heating operation, the refrigerant flows through the refrigerant piping 6 in the following order after exiting the compressor 2: four-way valve 3, indoor heat exchanger 5, expansion valve 4, and heat exchanger 1. The high-pressure gaseous refrigerant compressed by the compressor 2 is cooled by heat exchange with the indoor air (i.e., releases heat into the indoor air) and condenses as it flows into the indoor heat exchanger 5. The condensed gas-liquid mixed refrigerant has its pressure reduced as it passes through the expansion valve 4, becoming a low-pressure liquid refrigerant that is supplied to the heat exchanger 1. The liquid refrigerant that flows into the heat exchanger 1 is heated by heat exchange with the outside air (i.e., absorbs heat from the outside air) and evaporates, and the evaporated gas-liquid mixed refrigerant returns to the compressor 2 via the four-way valve 3.

[0020] (Defrosting operation) During heating operation, when the refrigerant evaporates in the heat exchanger 1, heat is removed from the outside air, causing water vapor in the outside air to condense into water droplets that adhere to the heat exchange components inside the heat exchanger 1 (for example, plate-shaped fins 11). If the outside air temperature is low, the attached moisture may freeze and form frost. In this case, the frost can obstruct heat exchange and reduce heat exchange efficiency, so a defrosting operation is performed to remove the frost.

[0021] During defrosting operation, the four-way valve 3 is set to the same state as during cooling operation, and the refrigerant is circulated in the same order as during cooling operation. However, both the outdoor fan 1' and the indoor fan 5' are stopped, and the heat exchange components of the heat exchanger 1 are heated by the high-temperature, high-pressure gaseous refrigerant sent from the compressor 2 to melt the frost, and the melted water is discharged from the heat exchanger 1 as drain water.

[0022] (Basic configuration of an outdoor heat exchanger) Figure 2 is a front view showing the configuration of the heat exchanger 1.

[0023] The heat exchanger 1 is a so-called fin-tube type heat exchanger, and is equipped with a heat exchanger core consisting of a fin-tube assembly in which heat transfer tubes 12 are assembled to plate-shaped fins 11. Figure 2 shows the configuration of the heat exchanger core with the housing 1a removed from the heat exchanger 1, and in Figure 2, the dashed line schematically shows the outer shape of the housing 1a.

[0024] In the heat exchanger 1 shown in Figure 2, the refrigerant flows in a left-right direction relative to the plane of the paper, and the direction of this refrigerant flow indicated by arrow X, which points from left to right relative to the plane of the paper, is defined as the X direction. In this embodiment, the X direction coincides with the stacking direction of the plate-shaped fins 11 and the extension direction of the heat transfer tubes 12, which will be described later. In addition, the outside air flowing into the heat exchanger 1 flows from front to back in a direction perpendicular to the plane of the paper, and the direction of this outside air flow, that is, the direction of arrow Z, which points from front to back relative to the plane of the paper, is defined as the Z direction. In this embodiment, the Z direction coincides with the short-side direction of the plate-shaped fins 11 and the insertion direction of the heat transfer tubes 12 into the plate-shaped fins 11, which will be described later. Furthermore, the direction of arrow Y, which points from top to bottom relative to the plane of the paper, is defined as the Y direction. Arrow Y is the vertically downward direction, that is, the direction of gravity, and coincides with the longitudinal direction of the plate-shaped fins 11 and the parallel direction of the heat transfer tubes 12, which will be described later.

[0025] The heat exchanger 1 comprises a plurality of plate-shaped fins 11, a plurality of heat transfer tubes 12, headers 13 and 14, a gas-side connector 15, and a liquid-side connector 16. In this embodiment, the plate-shaped fins 11 are substantially rectangular in shape. The headers 13 and 14 are cylindrical in shape, with their upper and lower ends in the Y direction sealed by a sealing material. The gas-side connector 15 is connected to a refrigerant pipe 6 (6b) connected to a four-way valve 3, and the liquid-side connector 16 is connected to a refrigerant pipe 6 (6c) connected to an expansion valve 4.

[0026] The refrigerant flowing into the heat exchanger 1 from the refrigerant piping 6 flows into one of the headers 13 and 14 via the gas-side fitting 15 or the liquid-side fitting 16, and is distributed to each of the multiple heat transfer tubes 12. As the refrigerant flows through the heat transfer tubes 12, it exchanges heat with the outside air flowing between the plate-shaped fins 11, and condenses or evaporates depending on the operating mode of the heat exchanger 1. The refrigerant after condensation or evaporation is collected in the other headers 14 and 13 and flows out to the refrigerant piping 6 via the liquid-side fitting 16 or the gas-side fitting 15.

[0027] (Detailed configuration of the fin tube assembly) Figure 3 is a schematic diagram showing an enlarged view of the fin tube assembly provided in the heat exchanger 1.

[0028] Figure 3(a) shows a side view of the fin tube assembly shown in Figure 2, viewed in the direction in which the multiple plate-shaped fins 11 are arranged, i.e., in the X direction which is the stacking direction of the plate-shaped fins 11. Figure 3(b) shows a rear view of the fin tube assembly shown in Figure 2, viewed downstream with respect to the direction of outside airflow, i.e., in the opposite direction to the Z direction which is the direction of outside airflow (i.e., in the reverse Z direction). Figure 3(c) shows a front view of the fin tube assembly shown in Figure 2, viewed upstream with respect to the direction of outside airflow, i.e., in the Z direction. Furthermore, Figure 3(d) shows a plan view of the fin tube assembly shown in Figure 2, viewed from above in a vertically downward direction, i.e., in the Y direction.

[0029] In this embodiment, the fin tube assembly comprises a plurality of plate-shaped fins 11 arranged at intervals from each other in the thickness direction of the plate-shaped fins 11, and a plurality of heat transfer tubes 12 that extend in the stacking direction of the plate-shaped fins 11, i.e., in a direction perpendicular to the surface of the plate-shaped fins 11, and are arranged so as to penetrate each of the plurality of plate-shaped fins 11 in the thickness direction of the plate-shaped fins 11. The plurality of heat transfer tubes 12 are arranged at intervals from each other in a direction perpendicular to the stacking direction of the plate-shaped fins 11, i.e., in the direction in which the heat transfer tubes 12 extend, i.e., in the vertical or gravity direction.

[0030] Here, the direction in which the heat transfer tube 12 extends is called the "extension direction" of the heat transfer tube 12, and it coincides with the stacking direction of the plate-shaped fins 11 in which the multiple plate-shaped fins 11 are arranged. The direction in which the multiple heat transfer tubes 12 are arranged is called the "parallel direction" of the heat transfer tubes 12, and in this embodiment, the direction perpendicular to both the extension direction and the parallel direction of the heat transfer tubes 12 coincides with the "direction of outside airflow". In this embodiment, the direction indicated by arrow X coincides with the stacking direction of the plate-shaped fins 11 and the extension direction of the heat transfer tube 12, the direction indicated by arrow Y coincides with the parallel direction of the heat transfer tubes 12, and the direction indicated by arrow Z coincides with the direction of outside airflow.

[0031] In actual use, the heat exchanger 1 is arranged and installed as shown in Figure 2, with the parallel direction Y of the heat transfer tubes 12 aligned with the vertical direction. In other words, the heat exchanger 1 is installed so that multiple plate-shaped fins 11 are arranged horizontally and multiple heat transfer tubes 12 are arranged vertically.

[0032] The heat transfer tube 12 has a flattened cross-sectional shape with a substantially oval or elliptical cross-section, and multiple internal passages 121 for circulating the refrigerant are formed in parallel to each other, extending in the extension direction X and aligned in the direction of outside air flow Z. Each end of the heat transfer tube 12 in the extension direction X is connected to headers 13 and 14, and the internal passages 121 communicate with header 13 at one end and with header 14 at the other end.

[0033] In this embodiment, the heat transfer tubes 12 are inserted into heat transfer tube insertion sections n, which are notches formed in each of the multiple plate-shaped fins 11, and are assembled to the plate-shaped fins 11 by being fixed to them by brazing or the like. Figure 3(a) shows a state in which some of the heat transfer tubes 12 have been removed in order to clearly show the heat transfer tube insertion sections n.

[0034] The heat transfer tube insertion section n has an opening that follows the shape of the outer surface of the heat transfer tube 12, formed parallel to the direction of outside air flow Z, such that it is open at one end edge 11a of the plate-shaped fin 11 in the direction of outside air flow and closed at the other end edge 11b. The heat transfer tube insertion section n ends between these two ends 11a and 11b, with the opposite side of the opening closed in the direction of outside air flow Z.

[0035] Here, the heat transfer tube 12 is formed such that the dimension defined in the direction of outside air flow Z, i.e., the width dimension Wt, is smaller than the dimension defined in the same direction of outside air flow Z for the plate-shaped fin 11, i.e., the width dimension Wf of the plate-shaped fin 11, and the dimension defined in the parallel direction Y of the heat transfer tube 12, i.e., the length dimension Lf (Figure 2), is larger than the width dimension Wf. Furthermore, if the dimension defined in the extension direction X of the heat transfer tube 12 for the plate-shaped fin 11 is defined as the thickness dimension, then the thickness dimension of the plate-shaped fin 11 is smaller than both its width dimension Wf and length dimension Lf.

[0036] The plate-shaped fin 11 has a continuous portion 112 that extends in the parallel direction Y of the heat transfer tube 12 between the heat transfer tube insertion portion n and the other end edge portion 11b, in other words, between the outer peripheral edge of the heat transfer tube 12 inserted into the heat transfer tube insertion portion n and the other end edge portion 11b.

[0037] The heat transfer tube insertion section n can be formed, for example, by punching out the plate-shaped fin 11 before forming the heat transfer tube insertion section n in the stretching direction X (in this embodiment, the opposite X direction, i.e., the opposite direction to the stretching direction X of the heat transfer tube 12) at the portion where the heat transfer tube insertion section n is to be formed. As the heat transfer tube insertion section n is formed, a collar 111 is formed on the peripheral edge surrounding the heat transfer tube insertion section n, protruding in the punching direction. The collar 111 guides the insertion of the heat transfer tube 12 into the heat transfer tube insertion section n and supports the heat transfer tube 12 after insertion.

[0038] Each of the multiple plate-shaped fins 11 has a stepped portion S that extends in the parallel direction Y of the heat transfer tube 12 between the outer edge of the heat transfer tube 12 inserted into the heat transfer tube insertion portion n and the continuous portion 112.

[0039] In this embodiment, both the continuous portion 112 and the stepped portion S of the plate-shaped fin 11 extend parallel to the edge portion 11b of the plate-shaped fin 11, and the direction in which the continuous portion 112 extends and the direction in which the stepped portion S extends are parallel to each other.

[0040] Furthermore, in this embodiment, the plate-shaped fin 11 has a plate portion between the stepped portion S and the edge portion 11a, the surface of which is formed flat in the ZY plane. Here, the outer edges of the heat transfer tubes 12, 12 that are adjacent to each other in the parallel direction Y (i.e., vertically) are connected in the direction of the flow of outside air Z by two imaginary straight lines parallel to the parallel direction Y of the heat transfer tubes 12. The portion enclosed by the lower surface of the heat transfer tube 12 located above, the upper surface of the heat transfer tube 12 located below, and these two imaginary straight lines is defined as the water storage region 113 of the plate portion. In Figure 3, the water storage region 113 is schematically shown by a dashed line.

[0041] As shown in Figure 3(d), the stepped portion S forms a step in the plate-shaped fin 11 in the thickness direction, that is, in the extension direction X of the heat transfer tube 12. In this embodiment, the step is formed on the plate portion of the plate-shaped fin 11 in the direction opposite to the protruding direction of the collar 111. As a result, the continuous portion 112 and the plate portion of the plate-shaped fin 11 are at different levels with the stepped portion S in between. In this embodiment, the continuous portion 112 and the plate portion are parallel to each other.

[0042] Furthermore, the stepped section S is spaced at intervals I1 in the direction of outside airflow Z for each of the heat transfer tubes 12 inserted into the heat transfer tube insertion section n. In other words, the intervals I1 are set in the width direction of the heat transfer tubes 12, and these intervals I1 are set to 3 mm or less.

[0043] Specifically, the distance I1 between the edge portion S1 of the stepped portion S that forms the boundary with the plate portion and the edge portion P of the outer circumference of the heat transfer tube 12 that is closest to the stepped portion S is 3 mm or less. In this embodiment, among the multiple heat transfer tubes 12 arranged in the parallel direction Y, the edge portions P closest to the stepped portion S are aligned with the parallel direction Y, in other words, they are positioned at equal distances from each other in the direction of outside air flow Z from the edge portion 11a of the plate-shaped fin 11, and the distance I1 between the edge portion S1 of the stepped portion S and the edge portion P of the outer circumference of the heat transfer tube 12 is 1 mm.

[0044] The heat exchanger 1 according to this embodiment has the above configuration. The effects obtained by this embodiment will be described below.

[0045] During heating operation, condensation occurs, and water droplets adhering to the surface of the plate-shaped fins 11 flow in the direction of gravity, i.e., in the parallel direction Y of the heat transfer tubes 12, during heating or defrosting operation, and accumulate on the upper surface of the heat transfer tubes 12 installed below. The water droplets or water masses formed by the accumulation of water droplets on the upper surface of the heat transfer tubes 12 flow from the upper surface of the heat transfer tubes 12 along the stepped section S to the lower end of the plate-shaped fins 11 in the direction of gravity, and are discharged from the heat exchanger 1 as drain. Here, the gap between the outer edge of the heat transfer tube 12 and the stepped section S, specifically the gap I1 between the edge P of the outer edge of the heat transfer tube 12 and the edge S1 of the stepped section S, is 3 mm or less, which allows for smooth flow from the upper surface of the heat transfer tube 12 to the stepped section S, making it possible to efficiently discharge water droplets. In Figure 3, the flow of water moving from the upper surface of the heat transfer tube 12 to the stepped section S and flowing down along the stepped section S is indicated by arrows F1 and F2.

[0046] Furthermore, by having a gap I1 of 1 mm or less between the outer edge P of the heat transfer tube 12 and the edge S1 of the stepped portion S, the flow from the upper surface of the heat transfer tube 12 toward the stepped portion S becomes smoother, making it possible to further improve drainage.

[0047] Figure 4 is an explanatory diagram showing the effect of forming a stepped portion S on the plate-shaped fin 11.

[0048] Figure 4 shows the results of a simulation in which the amount of water drained from the water storage area 113, which is sandwiched between heat transfer tubes 12, 12 arranged adjacently in the parallel direction Y, was calculated as the cumulative amount from the start of drainage. In the figure, the dashed line represents the case where the distance I1 between the outer edge P of the heat transfer tube 12 and the edge S1 of the stepped section S is 4 mm, the solid line represents the case where the distance I1 is 3 mm, the dotted line represents the case where the distance I1 is 2.5 mm, and the double dashed line represents the case where the distance I1 is 1 mm.

[0049] As shown in Figure 4, a significant improvement in the cumulative wastewater volume up to 0.1 seconds after the start of wastewater discharge is observed when the interval I1 is 3 mm or less, and the effect is particularly pronounced when the interval I1 is 1 mm or less. Specifically, it has been found that when the interval I1 is 3 mm, the cumulative wastewater volume after 0.1 seconds is more than five times greater compared to when the interval I1 is 4 mm.

[0050] (Second Embodiment) Figure 5 is a schematic diagram showing an enlarged view of the configuration of the fin tube assembly provided in the heat exchanger 1 according to the second embodiment of the present invention. The orientation of the displays in Figures 5(a) to 5(d) is the same as that shown in Figure 3.

[0051] In this embodiment, in addition to the configuration described above with respect to the first embodiment, the plate-shaped fin 11 has a slit 114 in each of the multiple water storage regions 113 sandwiched between multiple heat transfer tubes 12, which are arranged adjacent to each other in the parallel direction Y.

[0052] The slit 114 is formed with a gap between it and the heat transfer tube 12 located below it, and the gap between the slit 114 and the heat transfer tube 12 below it in the parallel direction Y of the heat transfer tubes 12, specifically the gap I2 between the lower end of the slit 114 and the upper surface of the heat transfer tube 12 below it, is set to 2 mm or more.

[0053] Furthermore, the slit 114 is set to have a dimension in the direction of outside airflow Z, that is, a width dimension W of 3 mm or more.

[0054] Furthermore, as shown in Figures 5(a) and (c), the slit 114 has a substantially rectangular intermediate portion 114a and an upper end portion 114b that extends upward in the opposite Y direction from the upper edge of the intermediate portion 114a, as viewed from the side of the heat exchanger 1 with the plate-shaped fins 11 in the extending direction X of the heat transfer tubes 12 and from the front of the heat exchanger 1 with the plate-shaped fins 11 in the direction of outside air flow Z. The upper end portion 114b is formed to extend diagonally with respect to the intermediate portion 114a. Specifically, in the ZY plane, the upper end portion 114b of the slit 114 extends from the upper edge of the intermediate portion 114a in the opposite direction to the parallel direction Y of the heat transfer tubes 12, and is inclined in the opposite direction to the outside air flow direction Z. In other words, the upper edge of the upper end portion 114b is closer to the continuous portion 112 than the lower edge that is in contact with the upper edge of the intermediate portion 114a.

[0055] Furthermore, in this embodiment, the dimension of the upper end 114b of the slit 114 defined in the parallel direction Y of the heat transfer tube 12, i.e., the length dimension L1, is in a relationship of L1 / L2 ≤ 1 / 5 with respect to the overall length dimension L2 of the slit 114.

[0056] In this embodiment, in addition to the above, a lower end portion 114c is provided that extends further downward in the Y direction from the lower edge of the intermediate portion 114a. As shown in Figure 5(a), the lower end portion 114c is formed to extend in the ZY plane from the lower edge of the intermediate portion 114a parallel to the parallel direction Y of the heat transfer tube 12. The lower end portion 114c is not limited to this, and like the upper end portion 114b, it may extend from the lower edge of the intermediate portion 114a in the parallel direction Y, and may be inclined in the opposite direction to the outside air flow direction Z, in other words, the lower edge of the lower end portion 114c is closer to the continuous portion 112 than the upper edge that is in contact with the lower edge of the intermediate portion 114a.

[0057] Furthermore, in a front view of the heat exchanger 1 with the plate-shaped fin 11 viewed in the direction of outside air flow Z, as shown in Figure 5(c), the intermediate portion 114a has dimensions in the XY plane that are determined in the extension direction X of the heat transfer tube 12 relative to the plate portion of the plate-shaped fin 11, that is, the cut-up height dimension. In this embodiment, the intermediate portion 114a is formed parallel to the parallel direction Y of the heat transfer tube 12 relative to the plate portion, while maintaining a constant distance in the extension direction X from the plate portion of the plate-shaped fin 11. The slit 114 can be formed, for example, by cutting and raising the plate portion of the plate-shaped fin 11.

[0058] As shown in Figure 5(c), the upper end portion 114b is formed to extend in the opposite direction to the parallel direction Y of the heat transfer tube 12 and to be inclined in the opposite direction to the extension direction X, so as to connect the upper edge of the intermediate portion 114a and the plate portion of the plate-shaped fin 11 in the XY plane, in other words, so as to gradually decrease the cut-up height dimension relative to the plate portion from the lower edge of the upper end portion 114b to the upper edge of the upper end portion 114b, and to be inclined in the opposite direction to the extension direction X. Similarly, the lower end portion 114c is formed to extend in the parallel direction Y of the heat transfer tube 12 and to be inclined in the opposite direction to the extension direction X, so as to connect the lower edge of the intermediate portion 114a and the plate portion of the plate-shaped fin 11, in other words, so as to gradually decrease the cut-up height dimension relative to the plate portion from the upper edge of the lower end portion 114c to the lower edge of the lower end portion 114c, and to be inclined in the opposite direction to the extension direction X.

[0059] According to this embodiment, in addition to the effects obtained by the first embodiment, the following effects can be obtained.

[0060] Firstly, by forming slits 114 in the water storage region 113 between the heat transfer tubes 12, 12 that are adjacent to each other in the parallel direction Y of the plate-shaped fins 11, it becomes possible to improve the heat exchange efficiency.

[0061] Secondly, by spacing the slit 114 and the heat transfer tube 12 below it, and setting the distance I2 between them to 2 mm or more, it is possible to avoid the slit 114 obstructing the flow of water droplets or water masses accumulated on the upper surface of the heat transfer tube 12, thereby ensuring a flow path for the water droplets or water masses and enabling smooth discharge from the heat exchanger 1. In other words, by setting the distance I2, it is possible to achieve both heat exchange efficiency and drainage.

[0062] Thirdly, by making the dimension of the slit 114 in the direction of outside airflow Z, that is, the width dimension W of the slit 114 3 mm or more, water droplets adhering to the slit 114 can easily flow along the surface of the slit 114, and by merging with other water droplets, for example, water droplets or water masses accumulated on the upper surface of the heat transfer tube 12, they are facilitated to flow down the stepped portion S, and can be smoothly discharged from the heat exchanger 1.

[0063] Fourth, by providing an intermediate portion 114a and an upper portion 114b in the slit 114, extending the upper portion 114b from the upper edge of the intermediate portion 114a in the opposite direction to the parallel direction Y of the heat transfer tubes 12, and further inclining it in the opposite direction to the outside air flow direction Z, that is, so that the upper edge of the upper portion 114b is closer to the continuous portion 112 than the lower edge, it becomes possible to extend the edge of the slit 114 facing the outside air flow while maintaining drainage, thereby further improving the heat exchange efficiency.

[0064] Fifth, in addition to the intermediate portion 114a and the upper end portion 114b, the slit 114 is further provided with a lower end portion 114c. The intermediate portion 114a rises parallel to the plate portion of the plate-shaped fin 11, maintaining a constant distance in the extension direction X of the heat transfer tube 12. The upper end portion 114b is inclined with respect to the plate portion so that the cut-up height dimension from the plate portion gradually decreases from its lower edge to its upper edge. Furthermore, the lower end portion 114c is inclined with respect to the plate portion so that the cut-up height dimension from the plate portion gradually decreases from its upper edge to its lower edge. By forming each of these, it becomes possible to extend the edge portion of the slit 114 facing the outside airflow while maintaining drainage, thereby further improving the heat exchange efficiency.

[0065] (Third embodiment) Figure 6 is a schematic diagram showing the configuration of a fin tube assembly provided in a heat exchanger 1 according to a third embodiment of the present invention.

[0066] Figure 6(a) shows a side view of the plate-shaped fin 11 as seen in the extension direction X of the heat transfer tube 12, Figure 6(b) is a cross-sectional view taken along the line VIb-VIb shown in Figure 6(a), and Figure 6(c) is a cross-sectional view taken along the line VIc-VIc.

[0067] The plate-shaped fin 11 is provided with a plurality of slits 114, 114' that differ in shape or the height of the cut-up from the plate portion of the plate-shaped fin 11 (indicated by reference numerals H1 and H2 in the cross-sectional view). Specifically, these plurality of slits 114, 114' include a first slit 114 and a second slit 114' which has a smaller cut-up height dimension H than the first slit 114, and the first slit 114 and the second slit 114' are arranged in the direction of outside air flow Z between heat transfer tubes 12, 12 that are adjacent to each other in the parallel direction Y.

[0068] In this embodiment, a first slit 114 with a relatively large cut-up height dimension H1 is positioned downstream with respect to the outside airflow direction Z, which is the direction of outside airflow between the plate-shaped fins 11, and a second slit 114' with a relatively small cut-up height dimension H2 is positioned upstream. The first slit 114 and the second slit 114' are aligned adjacent to each other in the outside airflow direction Z of the heat transfer tube 12, and in a front view in the outside airflow direction Z, that is, in a projection onto the XY plane, they overlap each other. The angles θ1 and θ2 at which the upper and lower ends of the first slit 114 and the second slit 114' are inclined with respect to the plate portion of the plate-shaped fin 11 are equal to each other. The angles θ1 and θ2 may be different from each other.

[0069] According to this embodiment, the following effects can be obtained in particular.

[0070] By arranging the first slit 114 and the second slit 114', which have different dimensions in the extension direction X of the heat transfer tube 12, that is, different cut-up height dimensions H, in two stages, front and back, adjacent to each other in the direction of outside air flow Z, it is possible to increase the overall surface area of ​​the slit 114 that comes into contact with the outside air, thereby improving the heat exchange efficiency.

[0071] In this embodiment, slits 114 and 114' of the same shape or cut-up height are formed in adjacent water storage regions 113, 113 in the parallel direction Y, with one heat transfer tube 12 in between. However, it is also possible to form slits 114 and 114' of different shapes or cut-up heights between adjacent water storage regions 113, 113 in the parallel direction Y. For example, a second slit 114' with the same cut-up height dimension may be formed in both the upper and lower water storage regions 113, 113, while the cut-up height dimension of the slit provided as the first slit 114 may be different between the upper and lower water storage regions 113, 113.

[0072] (Fourth Embodiment) Figure 7 is a schematic diagram showing the configuration of a fin tube assembly provided in a heat exchanger 1 according to the fourth embodiment of the present invention.

[0073] In this embodiment, the plate-shaped fin 11 comprises a first water storage region 113a in which slits 114 and 114' are formed, and a second water storage region 113b in which slits 114 and 114' are not formed.

[0074] In other words, when heat transfer tubes 12, 12 are arranged adjacent to each other in the parallel direction Y, a first pair of heat transfer tubes 12, 12 are formed, flanking a first water reservoir region 113a where slits 114, 114' are formed, and a second pair of heat transfer tubes 12, 12 are formed flanking a second water reservoir region 113b where slits 114, 114' are not formed. The first pair and the second pair are determined by different combinations of heat transfer tubes 12, 12, and this does not prevent one of the heat transfer tubes 12 in a pair from being common to both the first and second pairs.

[0075] In this embodiment, the first pair and the second pair consist of a pair of heat transfer tubes 12, 12 that sandwich adjacent water storage regions 113a and 113b in the parallel direction Y, with one heat transfer tube 12 common to both pairs. In other words, each heat transfer tube 12 aligned in the parallel direction Y is sandwiched between the first water storage region 113a and the second water storage region 113b, and one second water storage region 113b is sandwiched between the upper and lower first water storage regions 113a. However, it is not limited to this, and it is possible to form multiple second water storage regions 113b between the upper and lower first water storage regions 113a, and it is also possible to form multiple first water storage regions 113a between the upper and lower second water storage regions 113b.

[0076] According to this embodiment, the following effects can be obtained in particular.

[0077] In multiple pairs of heat transfer tubes 12, 12 adjacent to each other in the parallel direction Y, some pairs have slits 114, 114' in the water storage region 113 sandwiched between the upper and lower heat transfer tubes 12, 12, while others do not have slits 114, 114'. In other words, by not providing slits 114, 114' in the water storage region 113 (second water storage region 113b) sandwiched between some pairs of heat transfer tubes 12, 12, it is possible to maintain as much as possible the effect of improving heat exchange efficiency by providing slits 114, 114', while avoiding a situation where the flow of water droplets is excessively obstructed by the slits 114, 114', thereby achieving a balance between heat exchange efficiency and drainage.

[0078] (Fifth embodiment) Figure 8 is a schematic diagram showing the configuration of a fin tube assembly provided in a heat exchanger 1 according to the fifth embodiment of the present invention.

[0079] In this embodiment, multiple fin tube assemblies A1 and A2 are arranged in two stages, front and back, aligned in the direction of outside air flow Z. That is, the heat exchanger core comprises a first fin tube assembly A1 and a second fin tube assembly A2 arranged adjacent to the first fin tube assembly A1 on one side in the direction of outside air flow Z. The plate-shaped fins 11 and heat transfer tubes 12 constituting the first fin tube assembly A1 have the same shape as the plate-shaped fins 11 and heat transfer tubes 12 constituting the second fin tube assembly A2, except for the arrangement of the slits 114 and 114'.

[0080] In this embodiment, in the first fin tube assembly A1 and the second fin tube assembly A2, the first water storage region 113a, in which slits 114 and 114' are formed, and the second water storage region 113b, in which slits 114 and 114' are not formed, are arranged so that they are adjacent in the direction of outside air flow Z when the plate-shaped fins 11 are viewed in the direction of extension X of the heat transfer tube 12. Specifically, the second water storage region 113b of the second fin tube assembly is adjacent to the first water storage region 113a of the first fin tube assembly A1, and the first water storage region 113a of the second fin tube assembly is adjacent to the second water storage region 113b of the first fin tube assembly A1.

[0081] As a result, as shown in Figure 8, the first water storage region 113a and the second water storage region 113b are arranged in a staggered pattern in a side view, or in other words, diagonally opposite each other, between the four water storage regions 113a and 113b of the first fin tube assembly A1, which are adjacent to the first water storage region 113a and 113b in the parallel direction Y of the heat transfer tubes 12, and the two water storage regions 113b and 113a of the second fin tube assembly A2, which are adjacent to the first water storage region 113a and 113b in the direction Z of the outside air flow.

[0082] According to this embodiment, the following effects can be obtained in particular.

[0083] By arranging a first water storage region 113a having slits 114 and 114' and a second water storage region 113b without slits 114 and 114' in a staggered pattern in a side view between the first fin tube assembly A1 and the second fin tube assembly A2, it is possible to maintain as much as possible the effect of improving heat exchange efficiency by providing the slits 114 and 114', while avoiding excessive air resistance caused by the slits 114 and 114', which would cause stagnation in the flow of outside air inside the heat exchanger 1. Furthermore, it is possible to equalize the air resistance exerted by the slits 114 and 114' among the different plate-shaped fins 11, thereby avoiding a situation where the flow of outside air through the heat exchanger 1 becomes uneven.

[0084] (Sixth Embodiment) Figure 9 is a schematic diagram showing the configuration of a fin tube assembly provided in a heat exchanger 1 according to the sixth embodiment of the present invention. Figure 9(a) shows the configuration of the fin tube assembly in a side view with the plate-shaped fins 11 viewed in the extension direction X of the heat transfer tubes 12, and Figure 9(b) shows the plate-shaped fins 11 viewed from above in the parallel direction Y of the heat transfer tubes 12.

[0085] In this embodiment, similar to the fifth embodiment, the heat exchanger core comprises multi-stage fin tube assemblies A1 and A2.

[0086] In this embodiment, between the first fin tube assembly A1 and the second fin tube assembly A2, the first water storage region 113a, which has slits 114 and 114' formed thereon, and the second water storage region 113b, which does not have slits 114 and 114' formed thereon, are arranged such that in a plan view when the plate-shaped fins 11 are viewed from above in the parallel direction Y of the heat transfer tubes 12, they are adjacent in the direction of outside air flow Z. Specifically, the second water storage region 113b of the second fin tube assembly A2 is adjacent to the first water storage region 113a of the first fin tube assembly A1 in the direction of outside air flow Z, and the first water storage region 113a of the second fin tube assembly is adjacent to the second water storage region 113b of the first fin tube assembly A1 in the direction of outside air flow Z.

[0087] As a result, as shown in Figure 9(b), the first water storage region 113a and the second water storage region 113b are arranged in a staggered pattern in a plan view, or in other words, diagonally opposite each other, between the four water storage regions 113a and 113b: the two water storage regions 113a and 113b of the first fin tube assembly A1 adjacent to the extension direction X of the heat transfer tube 12, and the two water storage regions 113b and 113a of the second fin tube assembly A2 adjacent to these two water storage regions 113a and 113b in the outside air flow direction Z.

[0088] According to this embodiment, the following effects can be obtained in particular.

[0089] By arranging a first water storage region 113a having slits 114 and 114' and a second water storage region 113b without slits 114 and 114' in a staggered pattern in plan view between the first fin tube assembly A1 and the second fin tube assembly A2, it is possible to maintain as much as possible the effect of improving heat exchange efficiency by providing the slits 114 and 114', while avoiding excessive air resistance caused by the slits 114 and 114', which would cause stagnation in the flow of outside air inside the heat exchanger 1. Furthermore, it is possible to equalize the air resistance exerted by the slits 114 and 114' among the different plate-shaped fins 11, thereby avoiding a situation where the flow of outside air through the heat exchanger 1 becomes uneven.

[0090] In the above description, the step in the stepped portion S is formed in the direction opposite to the protruding direction of the collar 111. The step provided in the stepped portion S is not limited to this, and may also be formed in the direction of the protruding direction of the collar 111.

[0091] Furthermore, in the above explanation, the outside air was assumed to flow in the direction of outside air flow Z, indicated by arrow Z in Figure 2, that is, from front to back relative to the plane of the paper. However, the direction in which the outside air flows is not limited to this, and may also be in the opposite direction to the outside air flow direction Z, for example, in the front view shown in Figure 2, it may flow from back to front relative to the plane of the paper. In other words, the direction in which the notch of the heat transfer tube insertion section n opens is not limited to the downstream side with respect to the outside air flow, but may also be the upstream side.

[0092] Furthermore, although the headers 13 and 14 were formed from a single cylindrical member in the above description, the headers 13 and 14 are not limited to this and may be so-called laminated headers formed by stacking plate-shaped plates.

[0093] Furthermore, in the above description, the heat transfer tube insertion section n is formed to have a constant width over the entire direction of outside air flow Z and a length shorter than the heat transfer tube 12 in the direction of outside air flow Z. However, the shape of the heat transfer tube insertion section n can be anything as long as the heat transfer tube 12 can be inserted. For example, in the notch of the heat transfer tube insertion section n, the opening end near the edge 11a of the plate-shaped fin 11 can be slightly widened vertically to improve the workability when inserting the heat transfer tube 12 into the notch.

[0094] While several embodiments of the present invention have been described, these embodiments are merely illustrative and are not intended to limit the scope of the invention. These novel embodiments can be carried out in a variety of other forms, and various omissions, substitutions, or modifications can be made without departing from the spirit of the invention. These embodiments or their variations are included in the scope and spirit of the invention, as well as in the claims of the invention and its equivalents. [Explanation of symbols]

[0095] C...Refrigeration cycle device, 1...Heat exchanger (outdoor heat exchanger), 1a...Housing, 1'...Outdoor fan, 2...Compressor, 2a...Compressor body, 2b...Accumulator, 3...Four-way valve, 4...Expansion valve, 5...Indoor heat exchanger, 5'...Indoor fan, 6, 6a~6f...Refrigerant piping, 11...Plate fin, 111...Collar, 112...Continuous section, 113...Water storage area, 114...Slit, 114a...Intermediate section, 114b...Upper end, 114c...Lower end, 12...Heat transfer tube, 121...Internal passage, 13, 14...Header, 15...Gas side fitting, 16...Liquid side fitting, S...Stepped section, X...Extension direction of heat transfer tube, Y...Parallel direction of heat transfer tube, Z...Outside air flow direction, A1...First fin tube assembly, A2...Second fin tube assembly.

Claims

1. Multiple plate-shaped fins are arranged with gaps between them in the thickness direction, Each of the aforementioned plate-shaped fins extends through the thickness direction, and a plurality of heat transfer tubes are arranged at intervals from each other in a direction perpendicular to the thickness direction, A heat exchanger in which the plurality of heat transfer tubes are arranged in parallel with the parallel direction of the tubes being oriented vertically, The plate-shaped fin has a heat transfer tube insertion portion that is open at one end edge in the direction of outside air flow perpendicular to both the extension direction and the parallel direction of the heat transfer tube, and closed at the other end edge, The plate-shaped fin has a stepped portion between the other end edge and the heat transfer tube insertion portion, which extends in the parallel direction of the heat transfer tube and forms a step in the thickness direction, A heat exchanger in which the distance between the heat transfer tube insertion portion and the stepped portion, determined for each of the plurality of heat transfer tubes, is 3 mm or less.

2. The heat exchanger according to claim 1, wherein the aforementioned interval is 1 mm or less.

3. The heat exchanger according to claim 1 or 2, wherein the plate-shaped fins have slits in the water storage area sandwiched between the heat transfer tubes that are adjacent to each other in the parallel direction.

4. The heat exchanger according to claim 3, wherein the slit is spaced 2 mm or more apart from the heat transfer tube below it.

5. The heat exchanger according to claim 3 or 4, wherein the slit has a dimension of 3 mm or more in the direction of the outside airflow.

6. The aforementioned slit is In a side view of the plate-shaped fin as seen in the direction of extension of the heat transfer tube, the intermediate portion extends in the parallel direction of the heat transfer tube, The heat exchanger according to any one of claims 3 to 5, having an upper end portion provided above the intermediate portion and inclined with respect to the parallel direction of the heat transfer tubes in the side view.

7. The aforementioned slit is The first slit and A heat exchanger according to any one of claims 3 to 6, comprising: a second slit provided on one side of the first slit in the direction of the flow of outside air, and having dimensions in the direction of extension of the heat transfer tube that are different from those of the first slit.

8. The heat transfer tube is The first pair of heat transfer tubes adjacent to each other in the parallel direction, This includes a second pair of heat transfer tubes, which are adjacent in the parallel direction and are different from the first pair, The heat exchanger according to any one of claims 3 to 7, wherein the slit is provided between the heat transfer tubes of one of the first pair and the second pair.

9. The plurality of heat transfer tubes are assembled to each of the plurality of plate-shaped fins in the thickness direction, and a first fin tube assembly is assembled to penetrate them in the thickness direction. The assembly comprises a second fin tube assembly, which is arranged on one side of the first fin tube assembly in the direction of the outside airflow, with respect to the first fin tube assembly, the plurality of heat transfer tubes different from the first fin tube assembly are assembled so as to penetrate each of the plurality of plate-shaped fins different from the first fin tube assembly in the thickness direction, The heat exchanger according to any one of claims 3 to 8, wherein the first water storage region having the slit and the second water storage region not having the slit are arranged in a staggered pattern between the first fin tube assembly and the second fin tube assembly such that they are adjacent to each other in the direction of the outside air flow when the heat exchanger is viewed from the side in the direction of extension of the heat transfer tubes.

10. The plurality of heat transfer tubes are assembled to each of the plurality of plate-shaped fins in the thickness direction, and a first fin tube assembly is assembled to penetrate them in the thickness direction. The assembly comprises a second fin tube assembly, which is arranged on one side of the first fin tube assembly in the direction of the outside airflow, with respect to the first fin tube assembly, the plurality of heat transfer tubes different from the first fin tube assembly are assembled so as to penetrate each of the plurality of plate-shaped fins different from the first fin tube assembly in the thickness direction, The heat exchanger according to any one of claims 3 to 8, wherein the first water storage region having the slit and the second water storage region not having the slit are arranged in a staggered pattern between the first fin tube assembly and the second fin tube assembly such that they are adjacent to each other in the direction of the outside air flow when viewing the heat exchanger in a plan view in the parallel direction of the heat transfer tubes.

Images